Metering injector valve

ABSTRACT

A metering injector valve which may be used in internal combustion engine carburetor idle systems includes a first valve housing and a second valve housing integral therewith, a first axial passageway being provided within the first housing while a second axially extending passageway, interconnected with the first passageway at the downstream end and with a source of power-fluid at the upstream end, is similarly provided within the second housing. A metering ball is reciprocably disposed within the second passageway, and a diametrically extending passageway is provided within the rear portion of the first housing so as to be interconnected with the first passageway at its central portion and be open to the atmosphere at its outer portions. Under operative idle conditions, air and a metered amount of power-fluid may enter the diametrically extending passageway and the second axially extending passageway respectively, whereupon such fluids may mix and be conducted downstream of the first passageway so as to be injected into the carburetor idle passage whereby such air-power-fluid mixes with and atomizes the fuel being admitted to the carburetor barrel.

1U 1111a tates atent 1191 [111 3,34,675 Harrow Sept. M, 197 1 1 METERING INJECTOR VALVE [57] SACT [75] Inventor: Desmond J. Farrow, North East,

A metering injector valve which may be used in inter- 73 Assignee; T U i d States f A i as nal combustion engine carburetor, idle systems inrepresented b th Secretary of th cludes a first valve housing and a second valve housing Air Force, Washington, Dc. ns a tge g a aqua! p y p v1 e wt in t e irst ousmg w 1e a secon axia [22] Flled: 1973 extending passageway, interconnected with the first 21] Appl N 35 ,039 passageway at the downstream end and with a source of power-fluid at the upstream end, is similarly provided within the second housing. A metering ball is re- Tsz] Cl 2614/18 261/41 ciprocably disposed within the second passageway, 123/25 L and a diametrically extending passageway is provided [51] EH11. (:1. F 02m 15/02 within the rear portion of the first housing so as to be {58] Elem of Search 261/41 18 38; interconnected with the first passageway at its central 123/25 L portion and be open to the atmosphere at its outer portions. Under operative idle conditions, air and a [56] References Cited metered amount of power-fluid may enter the diamet- UNITED STATES PATENTS rically extending passageway and the second axially 1,752,859 4/1930 Simunek 123/15 L ex nding passageway respectively, whereupon such 2,970,822 2/ 1961 Ernest 261/D1G. 38 fluids may mix and be conducted downstream of the 3,313,532 4/1967 Carlson et a1 261/41 D first passageway so as to be injected into the carbure- 3,330,545 Donovan D tor passage whereby uch air-power fluid mixes 3,346,244 10/1967 Bess 261/63 with and atomizes the fuel being admitted to the can 3,348,823 10/1967 Roquerre 261/41 D buretor barrel. 3,749,376 7/1973 Alm et a1. 261/18 A Primary ExaminerTim R. Miles Attorney, Agent, or FirmObl0r1, Fisher, Spivak, McClelland & Maier 5 Claims, 1 Drawing Figure PATEN TED SEP 1 01974 METERING INJECTOR VALVE BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates generally to metering valves and more particularly to an improved metering injector valve which may be utilized in internal combustion engine carburetor idling systems.

2. Description of the Prior Art When an internal combustion engine is operating under idling, coasting or decelerating conditions, the butterfly throttle valve associated with the carburetor is substantially in the closed position. For practical considerations then, fuel can be supplied to the engine only by means of the carburetor idle system which bypasses the throttle valve, and although some air may also be bled into such system, the idling fuel-air mixture supplied to the engine is nevertheless found to be quite rich due to a relative insufficient supply of air. In addition, the mixture is also quite wet due to the fact that the air has failed to atomize the fuel properly, whereupon the fuel is more difficult to ignite within the engine cylinders which in turn leads to incomplete combustion, buildup of carbon deposits, and general inefficient and uneconomical operation of the engine.

Furthermore, conventional engines are often subject to the condition of dieseling or post-ignition wherein the engine is caused to continue to fire or ignite fuel even after the ignition has been turned off. Carbon is formed within the engine due to the function of the various anti-pollution equipment installed in conventional engines, such as for example, the PCV valve, and such carbon becomes heated to such an extent that it may continue to ignite the fuel even in the absence of an ignition spark. In addition, carbon and varnish tend to also accumulate when there is incomplete combustion of the fuel which of course discharges carbon monoxide into the atmosphere. Of equal importance, however, is the fact that such carbon build-up is never uniform within each engine cylinder and this condition can result in sticky valves and a generally rough operating engine with a consequent loss of power, excessive fuel consumption, generally poor engine performance, and even engine failure which would of course necessitate excessive repairs. Still further, carbon and varnish tend to accumulate within the idling parts of the carburetor causing the engine to idle roughly which usually necessitates the car being raced during the idle period in order to prevent the engine from stalling, and consequently such mode of operation also results in an excessive expenditure of fuel.

In addition, as is well known, existing gasolines cannot meet the precise requirements of the engine throughout the operational range from low to high speeds. At low speed, a high octane, slow burning, gasoline is desired, while at high speed, a low octane, fast burning gasoline is desired. A high octane, slow burning gasoline at high speed prevents the engine from attaining its predesigned peak performance and consequently causes excessive fuel consumption. A low octane, fast burning, gasoline at low speed may cause knock and consequent engine damage. Yet still further, as is also well known, one of the most dangerous products of combustion is the emission of oxides of nitrogen commonly known as NOx, which is generated as a re sult of the air within the combustion chambers becoming overheated. NOx in the atmosphere has been proven by medical experts to be one of the direct causes of many of our respiratory diseases.

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide an improved metering injector valve.

Another object of the present invention is to provide an improved metering injector valve which may be utilized in internal combustion engine carburetor idling systems.

Still another object of the present invention is to provide an improved metering injector valve which may be utilized in lieu of conventional carburetor idling screws. 1

Yet another object of the present invention is to provide an improved metering injector valve which will provide proper air fuel mixture to the engine under idling, coasting, or decelerating conditions.

Yet still another object of the present invention is to provide an improved metering injector valve which will serve to completely atomize the fuel supplied to the engine through the carburetor idle passage.

A further object of the present invention is to provide an improved metering injector valve which will permit the removal of harmful carbon and varnish deposits from the various engine components and prevent the formation of new deposits.

A still further object of the present invention is to provide an improved metering injector valve which will permit the engine to operate efficiently upon low oc tane gas with a concomitant increase in power, gas mileage, and fuel economy.

A yet further object of the present invention is to provide an improved metering injector valve which will permit the temperature within the engine combustion chambers to be materially lowered with the consequent prevention of NOx formation.

A still yet further object of the present invention is to provide an improved metering injector valve which permits the gasoline to be tailored to the requirements of the engine under the various operating load and speed conditions.

The foregoing objectives are achieved according to this invention through the provision of a metering injector valve having a first axial passageway extending through a first valve body portion, and a second axially extending passageway disposed within a second valve body portion integral with the first body portion and located eccentric to the first passageway. The downstream end of the second passageway is interconnected with the upstream end of the first passageway while the upstream end of the second passageway is connected to a source of power-fluid. The rear portion of the first valve body is also provided with a diametrical passageway which is open to the atmosphere and which also interconnects with the first axial passageway, and a reciprocably movable metering ball is disposed within the second passageway so as to regulate the flow of the power fluid in conjunction with the operating conditions of the engine. The central portion of the first valve body is conventionally externally threaded so as to threadedly engage the internally threaded bore of the carburetor body for permitting axial adjustment relative thereto whereupon the forward portion of the first valve body may, in conjunction with the idle discharge port provided within the carburetor body, meter the flow of fuel from the idle passage into the carburetor barrel. In this manner, a proper mixture of air and power-fluid is provided to the carburetor idle discharge port under idling, coasting, or decelerating conditions through the downstream end of the first passageway, so as to permit atomization of the fuel.

BRIEF DESCRIPTION OF THE DRAWING Various other objects, features, and attendant advantages of the present invention will be more fully appreciated as the same becomes better understood from the following detailed description when considered in connection with the accompanying drawing, wherein:

The sole FIGURE is a longitudinal cross-section view of a metering injector valve constructed according to this invention and showing its component parts, taken along the plane common to the axes of both axially extending bores.

DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT Referring now to the sole FIGURE, there is shown a metering injector valve, generally indicated by the reference character 10, comprising a first valve body portion and a second valve body portion integrally formed with the first valve body portion, generally indicated by the reference characters I2 and M, respectively. The first valve body portion 12 in turn comprises three integrally connected, substantially cylindrical portions 16, IS, and 20, the diameters of which progressively increase in a step-wise fashion from the downstream end of the body 12 toward the upstream end of the body. The central portion I8 of valve body 12 is conventionally externally threaded as at 22 so as to facilitate threaded engagement with an internally threaded bore, not shown, of the carburetor body, whereupon the metering valve may be suitably axially moved and adjusted relative to the carburetor body whereby the forward portion I6 of valve body 12 may, in conjunction with the idle discharge port, also not shown, provided within the carburetor body, meter the flow of fuel from the idle passage to the carburetor barrel. To facilitate the threading of valve portion 18 relative to the carburetor body, the rear portion 23 of valve body M may be knurled so as to enable the valve to be rotated either by hand or by suitable wrench-type tools.

An axially extending bore 24 is provided within body portion 14, the downstream end of the bore being connected to the upstream end of an axial bore 26 similarly provided within body portion 12, while the upstream end of bore 24 is connected to a source of fluid, not shown, such fluid comprising for example, a mixture of water, alcohol, and suitable additives, and hereinafter referred to as the power-fluid. Cylindrical portion is likewise centrally provided with a diametrically extending bore 28 which is open to the atmosphere at its outer extremities and is interconnected with axial bore 26 at its central portion, and consequently, depending upon the operating conditions of the engine, bore 26 serves as a fluid passageway for an air-power-fluid mixture which naturally exits from the bore at the downstream end 30. In this manner, the air-power-fluid mixture may atomize and further mix with the fuel metered by the forward portion 16 of the valve as noted heretofore.

In order to additionally meter the flow of the powerfluid so as to provide only a predetermined amount of such fluid and to further insure that such fluid is conducted through passageway 24 only at the appropriate times in accordance with the operating conditions of the engine, a metering ball 32 is disposed within passageway 24, the diameter of the ball being slightly less than the diameter of the passageway 24 so as to permit reciprocal movement of the ball within the passageway under the engines operative pressures. It will be further noted that in order to prevent the ball 32 from seating relative to passageway 26 and thereby terminat' ing the flow of power-fluid into such passageway, the diameter of passageway 24 is larger than the diameter of passageway 26, and in addition, the bore defining passageway 24 is located eccentric to the bore defining passageway 26. Consequently, as the ball reciprocates, a self-cleaning process is imparted thereto whereupon build-up of particles upon the ball, which could adversely affect its seating and therefore its metering operation, is prevented.

In order to further insure that the ball 32 does not seat relative to passageway 26, the walls of the valve portions 12 and I4 defining the juncture of bores 24 and 26 are formed so as to in fact provide the juncture with an irregular composite surface configuration comprising a planar portion 34 inclined toward the axis of portion 12 and extending in the downstream direction and an integral arcuate portion 36. Similarly, in order to prevent the expulsion of the ball 32 from bore 24 under the engine operational pressures, the rear end face portion of valve body 14 may be coined or swaged so as to provide flanged members 38, the diametrical extent therebetween of course being less than the diameter of ball 32. The flanged members 38 are somewhat inclined in the upstream direction so as to also serve as seating means for the ball 32 which under appropriate operational conditions can become seated so as to terminate the flow of the power-fluid.

In operation, when the engine is in the idling, coasting, or decelerating states, the butterlfy throttle valve, not shown, associated with the carburetor is substantially closed and consequently fuel is supplied to the engine by means of the carburetor idle system. The vacuum produced in the intake manifold and carburetor by means of the engine pistons will tend to draw fuel through the carburetor idle passage, not shown, and in addition, will, through means of the created suction and pressure differential, also unseat ball 32 from the flanged seating means 38 thus permitting the entrance of power-fluid into passageway 24. Such fluid naturally flows downstream into passageway 26 whereupon it is caused to mix with the air which is also being induced into passageway 26 through means of transverse passageway 28. Such mixture then of course exits from the downstream end 30 of passageway 26 whereupon it may thoroughly comingle with and atomize the fuel being drawn through the carburetor idle passage prior to such fuel entering the carburetor barrel and intake manifold.

In this manner, then, additional air is being supplied under idling, coasting, or decelerating conditions, so as to supplement any air which may be conventionally bled into the system through conventional idle air bleed ports. In view of the fact that the valve It) may also be axially adjusted relative to the carburetor body and idle discharge port so as to adjust the amount of fuel drawn through the carburetor idle passage, and that with the valve of the present invention sufficient air is able to be supplied under the noted conditions, a leaner or richer air-fuel mixture may be insured as desired. In addition, due to the atomization of the fuel prior to its induction into the carburetor barrel and intake manifold, ignition and more complete combustion of fuel within the cylinders is facilitated.

Furthermore, the introduction of the power-fluid into the carburetor, intake manifold, and ultimately the engine cylinders, serves to substantially increase the performance of the engine, as well as increase gas mileage, and optimize fuel consumption and combustion thereby materially reducing air pollution. Upon the introduction of the power-fluid into the combustion chambers, such fluid becomes a solvent which cleans valves and valve seats of carbon and varnish deposits and prevents the formation of new deposits. Consequently, conventional engine problems, such as for example, dieseling or post-ignition, sticky valves, and a generally rough engine operation can be simply and quickly eliminated.

Still further, as is well known, one of the most dangerous products of combustion is the production of oxides of nitrogen commonly known as NOX, which is generated due to the air within the combustion chambers becoming overheated. introduction of the powerfluid into the combustion chambers materially lowers the combustion temperature due to operational principles similar to those upon which refrigeration is based. The high heat of vaporization of a metered quantity of power-fluid serves to chill the air with which it is mixed and consequently lower the overall combustion temperature within the combustion chambers.

When the butterfly throttle valve is initially opened, and the engine speed increases, additional fuel is drawn into the carburetor venturi through means of the main metering system, the vacuum tends to decrease within the intake manifold and carburetor barrel, and consequentiy the pressure differential acting upon the metering ball 32. decreases, whereupon the pressure impulse created as a result of the equalized pressure will cause ball 32 to become seated with respect to seating means 3% thereby terminating the flow of the power fluid, as well as substantially rendering ineffective the entire idle system. As the engine speed is substantially increased, however, so as to cause a high degree of vacuum within the intake manifold and carburetor barrel and a consequent sharp pressure differential upon the metering ball 32, the ball will once again become unseated from the valve seat 38 and a supplemental quantity of fuel, air and power fluid will flow through the idle system.

Appreciation of the present invention then, renders it further apparent that in addition to obtaining increased engine performance, gas mileage, and lower pollutant emissions, conventional production engines may now be able to operate efficiently upon low octane gas throughout all speed ranges due to the fact that the power fluid serves to tailor the gasoline to meet the various engine requirements. There has never been a gasoline produced which has been able to meet the precise requirements of the engine throughout the entire speed range because at low speed the engine requires a high octane or slow burning gasoline while at high speed, the engine requires a low octane or fast burning gasoline. A high octane gasoline at high speed prevents the engine from attaining its peak performance and causes excessive fuel consumption, while a low octane gasoline at low speed will knock and possibly cause engine t damage.

Since the injection of the power-fluid raises the octane rating of the fuel, and as the greatest concentration of power-fluid within the fuel mixture occurs at low speeds, the engine in effect is provided with a high octane fuel when required. Similarly, at high speeds, when a low octane fuel is desired, although some power-fluid is in fact introduced into the engine, the proportional amount introduced is quite small and consequently the effective octane rating of the resulting fuel mixture is low, the power fluid being introduced for the purposes of obtaining the other beneficial effects noted heretofore, such as for example, prevention of carbon and varnish deposits, lowering the combustion temperature with the combustion chambers, and the like.

Obviously, many modifications and variations of the present invention are possible in light of the above teachings. It is to be understood therefore, that within the scope of the appended claims the present invention may be practiced otherwise than as specifically described herein.

What is claimed as new and desired to be secured by letters patent of the United States is:

l. A metering injector valve which may be used in internal combustion engine carburetor idle systems having an idle discharge port, comprising:

a first valve housing provided with a first axial passageway;

a second valve housing provided with a second axially extending passageway, the downstream end of said second passageway being interconnected with said first passageway while the upstream end of said second passageway is capable of being connected to a source of power-fluid;

metering ball means disposed within said second passageway for metering the supply of said powerfluid; and

means defining a diametrically extending passageway within said first housing, the central portion of said diametrically extending passageway being interconnected with said first passageway while the radial extremities of said diametrically extending passageway are open to the atmosphere,

whereby under engine idling conditions, a metered amount of said power-fluid may be supplied through said second passageway so as to mix with air supplied through said diametrically extending passageway and said air-power-fluid may be further conducted through said first passageway so as to be supplied to said carburetor idle discharge port.

2. A metering injector valve as :set forth in claim 1,

wherein said first valve housing further comprises:

downstream section means for cooperating with said carburetor idle discharge port so as to meter the supply of fuel to said carburetor;

upstream section means; and

externally threaded central section means interposed between and integral with said downstream and upstream sections for threadedly engaging internally threaded means of said carburetor,

whereupon rotation of said valve and said central section means causes said valve and said downstream section means to be axially adjusted relative to said carburetor so as to meter the supply of fuel to said carburetor, said air-power-fluid mixture fur ther mixing with and atomizing said fuel.

3. A metering injector valve as set forth in claim 2, wherein said diametrically extending passageway is centrally disposed within said upstream section means.

d. A metering injector valve as set forth in claim 1, wherein:

said second passageway is located eccentric to, and has a diameter greater than, said first passageway; and the diameter of said metering ball is slightly less than the diameter of said second passageway, whereby said metering ball is permitted to move in a reciprocal fashion within said second passageway to said first passageway. 

1. A metering injector valve which may be used in internal combustion engine carburetor idle systems having an idle discharge port, comprising: a first valve housing provided with a first axial passageway; a second valve housing provided with a second axially extending passageway, the downstream end of said second passageway being interconnected with said first passageway while the upstream end of said second passageway is capable of being connected to a source of power-fluid; metering ball means disposed within said second passageway for metering the supply of said power-fluid; and means defining a diametrically extending passageway within said first housing, the central portion of said diametrically extending passageway being interconnected with said first passageway while the radial extremities of said diametrically extending passageway are open to the atmosphere, whereby under engine idling conditions, a metered amount of said power-fluid may be supplied through said second passageway so as to mix with air supplied through said diametrically extending passageway and said air-power-fluid may be further conducted through said first passageway so as to be supplied to said carburetor idle discharge port.
 2. A metering injector valve as set forth in claim 1, wherein said first valve housing further comprises: downstream section means for cooperating with said carburetor idle discharge port so as to meter the supply of fuel to said carburetor; upstream section means; and externally threaded central section means interposed between and integral with said downstream and upstream sections for threadedly engaging internally threaded means of said carburetor, whereupon rotation of said valve and said central section means causes said valve and said downstream section means to be axially adjusted relative to said carburetor so as to meter the supply of fuel to said carburetor, said air-power-fluid mixture further mixing with and atomizing said fuel.
 3. A metering injector valve as set forth in claim 2, wherein said diametrically extending passageway is centrally disposed within said upstream section means.
 4. A metering injector valve as set forth in claim 1, wherein: said second passageway is located eccentric to, and has a diameter greater than, said first passageway; and the diameter of said metering ball is slightly less than the diameter of said second passageway, whereby said metering ball is permitted to move in a reciprocal fashion within said second passageway but is nevertheless prevented from seating relative to said first passageway so as not to prematurely terminate the supply of power-fluid to said first passageway.
 5. A metering valve as set forth in claim 4, wherein said first valve housing and said second valve housing means defining said interconnection of said first and second passageways includes a planar surface inclined toward the axis of said first housing in the downstream direction and an integral arcuate surface, whereby said metering ball is further prevented from seating relative to said first passageway. 